EP0359514A2 - Mehrstufiger Zentrifugalverdichter - Google Patents

Mehrstufiger Zentrifugalverdichter Download PDF

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Publication number
EP0359514A2
EP0359514A2 EP89309233A EP89309233A EP0359514A2 EP 0359514 A2 EP0359514 A2 EP 0359514A2 EP 89309233 A EP89309233 A EP 89309233A EP 89309233 A EP89309233 A EP 89309233A EP 0359514 A2 EP0359514 A2 EP 0359514A2
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EP
European Patent Office
Prior art keywords
stage
diffuser
vaned
diffusers
vanes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP89309233A
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English (en)
French (fr)
Other versions
EP0359514B1 (de
EP0359514A3 (en
Inventor
Hiromi 9-506 Tsukubahouse Kobayashi
Hideo Nishida
Haruo Miura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
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Hitachi Ltd
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Filing date
Publication date
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0359514A2 publication Critical patent/EP0359514A2/de
Publication of EP0359514A3 publication Critical patent/EP0359514A3/en
Application granted granted Critical
Publication of EP0359514B1 publication Critical patent/EP0359514B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors

Definitions

  • This invention relates to multistage centrifugal compressors of the single axis type, wherein diffusers are provided radially outwardly from the impellers.
  • the compressors are of a high-pressure type, typically having a design operating outlet pressure of at least 50 atmospheres.
  • Such compressors are used for compressing gases in for example the chemical industry for injecting gases, in oil fields for air compression and in gas pipelines.
  • Vaneless diffusers have been used. Vaned diffusers are widely used in low-pressure compressors, both in single stage and multistage compressors. In these compressors, the ratio r/R of the outlet radius of an impeller R to the diffuser vane leading edge radius r is constant at all stages. Multistage centrifugal compressors of this kind are discussed in "Blower and Compressor", by Takefumi Ikui (published by Asakura Shoten, issued on June 25th, 1974).
  • Diffusers with vanes have not been adopted for high-pressure compressors, because a multistage centrifugal compressor having vaned diffusers has a high maximum efficiency but a narrow operating range.
  • the passage width becomes smaller toward the delivery since its volume flow rate becomes smaller.
  • the specific speed of an impeller at rear stages is smaller than that of an impeller at front stages.
  • the pressure is higher and the specific speed is smaller at a rear stage in a multistage centrifugal compressor, and the phenomenon called "rotating stalls" often occurs at the rear stage side.
  • a rotating stall in a vaneless diffuser is generated when the flow is reduced in a certain compressor stage and the average flow angle ⁇ at a diffuser inlet of the stage becomes less than the prescribed value.
  • reverse flow initiates locally at the boundary layers in the diffuser passage and develops into the main flow.
  • the stall area rotates around the axis at low frequency.
  • the stable driving range is at a larger flow rate than Qc. This means that the operating range becomes narrow compared with the case where a rotating stall is assumed not to occur, in which stable operation is possible at a flow rate greater than Qa.
  • the object of the present invention is to prevent generation of rotating stalls in the diffusers of a high pressure multistage centrifugal compressor, and thus provide a compressor which can be driven stably with high efficiency over a wide operating range.
  • the invention adopts vaned diffusers and, in respect of at least two stages, increases the ratio r/R of the outlet radius R of the centrifugal impellers to the diffuser vane leading edge radius r from the rear stage side (delivery side) toward the front stage side (suction side).
  • the ratio r/R and h/R, where h is the axial passage height of the diffuser (vane axial height) are selected so as to satisfy the following h/R ⁇ 0.04 r/R ⁇ 1 + 3.3h/R.
  • vanes When vanes are provided in accordance with these principles, the flow is forcibly directed by the vane towards the radial direction, and there is hardly any reverse flow. That is to say, the diffuser with vanes has the effect of preventing reverse flow by providing a vane front edge at the inner side of the position where reverse flow is generated first in case of a vaneless configuration.
  • a multi-stage centrifugal compressor having a shaft rotatable on an axis, a plurality of centrifugal impellers fixed on said shaft and having outlets at their peripheries, and conduits connecting said impellers to form a path for fluid undergoing multi-stage compression by said impellers from a suction side to a delivery side of the compressor.
  • the conduits include a plurality of diffusers arranged radially outwardly from the impellers, each impeller and its associated diffuser constituting a stage. At least two of said diffusers are in the form of vaned diffusers.
  • a first one has a ratio of diffuser vane leading edge radius to impeller outlet radius larger than the same ratio of a second one which is closer along said path to the delivery side than the first one.
  • the ratio of diffuser vane leading edge radius to impeller outlet radius preferably increases from each of the vaned diffusers to the next one along the fluid compression path in the direction from the delivery side to the suction side.
  • the ratio of the axial height of the vanes to the impeller outlet radius is less than 0.04, and may be less than 0.03.
  • each stage having a vaned diffuser r/R ⁇ 1 + 3.3 h/R wherein h is the axial height of the vanes, R is the impeller outlet radius, and r is the diffuser vane leading edge radius.
  • stages having vaned diffusers there may be at least one stage having a vaneless diffuser, closer to the suction side than the vaned diffusers.
  • the compressor of the invention typically has a design operating delivery pressure of at least 50 atmospheres, and in many cases at least 100 atmospheres.
  • the ratio of the outlet radius of the vanes to the inlet radius of the vanes is not more than 1.2, and the maximum thickness of each vane is preferably in the range 5 to 12% of the chord length of the vane.
  • the number of vanes is in the range 10 to 30, preferably 12 to 20.
  • vanes extend the full axial height of the diffuser.
  • the invention provides a multi-stage centrifugal compressor having a shaft rotatable on an axis, a plurality of centrifugal impellers fixed on said shaft and having outlets at their peripheries, and conduits connecting said impellers to form a path for fluid undergoing multi-stage compression by said impellers from a suction side to a delivery side of the compressor.
  • the conduits include a plurality of diffusers arranged radially outwardly from the impellers each impeller and its associated diffuser constituting a stage. At least two of the diffusers are vaned diffusers.
  • each vaned diffuser and its associated impeller h/R ⁇ 0.04 and r/R ⁇ 1 + 3.3h/R
  • h is the axial height of the vanes
  • R is the impeller outlet radius
  • r is the diffuser vane leading edge radius
  • a rotating shaft 1 is installed in a casing 3 on bearings 2.
  • Centrifugal impellers 4 (first stage 4a, second stage 4b, third stage 4c, fourth stage 4d) are carried by the shaft 1.
  • the impeller outlet radius R is the same in all four stages, and the axial height h of the diffuser passage is decreased according to the change of volume flow rate.
  • the outlet and the inlet of each adjacent pair of impellers 4 in the sequence are connected by passages 5 (first stage 5a, second stage 5b, third stage 5c) formed in the casing 3.
  • the inlet of the centrifugal impeller 4a of the front stage is connected to an inlet port 6 of the casing 3 and the outlet of the centrifugal impeller 4d at the rear stage (delivery side) is connected to an outlet port 7 of the casing 3.
  • vaned diffusers 8 first stage 8a, second stage 8b, third stage 8c, fourth stage 8d
  • return channels 9 first stage; 9a, second stage; 9b, third stage; 9c
  • Figs. 3 and 4 indicate relative values of the outlet radius R of the impellers 4, the height h of the vaned diffusers 8 and the leading edge radius r of the diffuser vanes. These values satisfy the following relation:- r/R ⁇ 1 + 3.3 h/R (1)
  • the radius at the rear edge of the diffuser vanes is not explicitly specified.
  • a rotating stall is generated in the diffuser when this reverse flow develops and forms a stall zone which rotates in the diffuser. Accordingly, if the first reverse flow is restrained in the diffuser, rotating stalls can be prevented.
  • the vaned diffusers 8 prevent rotating stalls without the reduction of the passage height h required for the vaneless diffusers, and the passage length passing through the diffusers is also shortened and friction loss is small. Therefore a high level of efficiency can be obtained since the flow is forcibly directed by the vanes and flow angle is large.
  • rotating stalls can be prevented in all stages and a multistage centrifugal compressor that achieves high efficiency and can be operated stably over a wide range is obtained.
  • Figs. 5 and 6 is a multistage centrifugal compressor with five stages in which intercooling of the fluid is carried out between the low pressure stage side and the high pressure stage side.
  • the same reference numbers are used to designate parts corresponding to the parts shown in Figs. 1 and 2.
  • Centrifugal impellers 11 (first stage 11a, second stage 11b, third stage 11c) of the high pressure stage side group with the same outlet radius R as well as centrifugal impellers 10 (first stage 10a, second stage 10b) of the low pressure stage side group with the same outlet radius R are fixed on the rotational shaft 1.
  • the low pressure stage side group has vaneless diffusers 12 (first stage 12a, second stage 12b) and a return channel 13
  • the high pressure stage side group has vaned diffusers 14 (first stage 14a, second stage 14b, third stage 14c) and return channels 15 (first stage 15a, second stage 15b).
  • vaneless diffusers are used for the low pressure stage side group and vaned diffusers for the high pressure stage side group is as follows.
  • the impellers of this multistage centrifugal compressor have a wide range of specific speeds. Since at the low pressure stage side (front stage side) the specific speed is large and the flow angle of the diffusers is large for design convenience, rotating stalls hardly occur. At the low pressure level, even if a rotating stall is generated, its small shaft exciting force does not cause a problem.
  • vaned diffusers are provided for the high pressure stage group where rotating stalls cause a problem, and the leading edge radius ratio of each diffuser is set as shown in Fig. 6.
  • rotating stalls in the diffusers can be prevented in the three stages on the rear stage side, and the compressor properties of high efficiency and a wide stable driving range can be obtained.
  • FIG. 7 is the same as that of Figs. 5 and 6 except that vaned diffusers are used at the low pressure stage side group.
  • the ratio r/R of the leading edge radius r of these diffuser vanes 16 to the centrifugal impeller outlet radius R is constant.
  • Vaned diffusers are used in the high pressure stage side group and the ratio r/R of the leading edge radius r of the diffuser vanes 14 (first stage 14a, second stage 14b) to the impeller outlet radius R satisfy the relationship with the ratio h/R of the diffuser vane height h to the impeller outlet radius R as follows:- r/R ⁇ l + 3.3 h/R and the ratio r/R increases from the rear stage side to the front stage side in this group.
  • Tables 1 and 2 Dimensions and design operating conditions of two multistage compressors of the invention are given in Tables 1 and 2 below.
  • the compressors are generally as shown in Fig. 1; the compressor of Table 1 has four stages, whereas the compressor of Table 2 has three stages.
  • Table 1 1st stage 2nd stage 3rd stage 4th stage Impeller outlet radius R 85 mm 85 mm 75 mm 75 mm Vane leading edge radius r 93.5mm 91.8mm 78.5mm 77.5mm Vane trailing edge radius r′ 107.5mm 105.5mm 90.3mm 98 mm Number of vanes 18 18 18 18 Vane height in axial direction h 3.0mm 2.6mm 2.0mm 1.8mm Radius ratio r / R 1.1 1.08 1.047 1.033 Height ratio h / R 0.035 0.031 0.027 0.024 Shaft rotational speed : 14370 rpm Gas : CO2 Pressure Suction/Delivery : 45/140 atmospheres Table 2 1st stage 2nd stage 3rd stage Impeller outlet radius

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP89309233A 1988-09-14 1989-09-12 Mehrstufiger Zentrifugalverdichter Expired - Lifetime EP0359514B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP63228745A JPH0646035B2 (ja) 1988-09-14 1988-09-14 多段遠心圧縮機
JP228745/88 1988-09-14

Publications (3)

Publication Number Publication Date
EP0359514A2 true EP0359514A2 (de) 1990-03-21
EP0359514A3 EP0359514A3 (en) 1990-07-04
EP0359514B1 EP0359514B1 (de) 1992-12-23

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP89309233A Expired - Lifetime EP0359514B1 (de) 1988-09-14 1989-09-12 Mehrstufiger Zentrifugalverdichter

Country Status (5)

Country Link
US (1) US4938661A (de)
EP (1) EP0359514B1 (de)
JP (1) JPH0646035B2 (de)
CN (1) CN1015489B (de)
DE (1) DE68904020T2 (de)

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EP1311315A1 (de) * 2000-07-05 2003-05-21 Compumedics Sleep Pty. Ltd. Doppel-druck ventilator für eine druckluftvorrichtung
EP1990544A2 (de) 2007-05-10 2008-11-12 Hitachi Plant Technologies, Ltd. Mehrstufen-Zentrifugalkompressor
EP2149709A3 (de) * 2008-07-30 2011-10-12 Hitachi Plant Technologies, Ltd. Mehrstufiger Rotationsverdichter
CN104632645A (zh) * 2014-11-06 2015-05-20 沈阳斯特机械制造有限公司 一种双向进气多级离心压缩机
EP2977619A4 (de) * 2013-03-21 2016-12-21 Mitsubishi Heavy Ind Ltd Kreiselmaschine für fluide
RU183324U1 (ru) * 2017-12-29 2018-09-18 федеральное государственное автономное образовательное учреждение высшего образования "Санкт-Петербургский политехнический университет Петра Великого" (ФГАОУ ВО "СПбПУ") Безлопаточный диффузор малорасходной центробежной компрессорной ступени
WO2019160550A1 (en) * 2018-02-15 2019-08-22 Dresser-Rand Company Centrifugal compressor achieving high pressure ratio
CN112177949A (zh) * 2019-07-04 2021-01-05 三菱重工业株式会社 多级离心压缩机

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US5071317A (en) * 1990-06-04 1991-12-10 Alan Leach Centrifugal pump having a unitary one-piece diffusion casing and a unitary one piece turbine impeller unit
US5125806A (en) * 1990-06-18 1992-06-30 Sundstrand Corporation Integrated variable speed compressor drive system
DE4115805A1 (de) * 1991-05-15 1992-11-19 Bosch Gmbh Robert Radialgeblaese mit einem in einem spiralgehaeuse umlaufenden geblaeserad
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EP0571739B1 (de) * 1992-05-28 1997-10-15 Nikkiso Co., Ltd. Axial-Diffusor für eine Kreiselpumpe
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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1311315A1 (de) * 2000-07-05 2003-05-21 Compumedics Sleep Pty. Ltd. Doppel-druck ventilator für eine druckluftvorrichtung
EP1311315A4 (de) * 2000-07-05 2006-04-05 Compumedics Sleep Pty Ltd Doppel-druck ventilator für eine druckluftvorrichtung
EP1990544A2 (de) 2007-05-10 2008-11-12 Hitachi Plant Technologies, Ltd. Mehrstufen-Zentrifugalkompressor
EP1990544A3 (de) * 2007-05-10 2009-06-17 Hitachi Plant Technologies, Ltd. Mehrstufen-Zentrifugalkompressor
US8287236B2 (en) 2007-05-10 2012-10-16 Hitachi Plant Technologies, Ltd. Multistage centrifugal compressor
EP2149709A3 (de) * 2008-07-30 2011-10-12 Hitachi Plant Technologies, Ltd. Mehrstufiger Rotationsverdichter
EP2977619A4 (de) * 2013-03-21 2016-12-21 Mitsubishi Heavy Ind Ltd Kreiselmaschine für fluide
US10197063B2 (en) 2013-03-21 2019-02-05 Mitsubishi Heavy Industries Compressor Corporation Centrifugal fluid machine
CN104632645A (zh) * 2014-11-06 2015-05-20 沈阳斯特机械制造有限公司 一种双向进气多级离心压缩机
RU183324U1 (ru) * 2017-12-29 2018-09-18 федеральное государственное автономное образовательное учреждение высшего образования "Санкт-Петербургский политехнический университет Петра Великого" (ФГАОУ ВО "СПбПУ") Безлопаточный диффузор малорасходной центробежной компрессорной ступени
WO2019160550A1 (en) * 2018-02-15 2019-08-22 Dresser-Rand Company Centrifugal compressor achieving high pressure ratio
CN112177949A (zh) * 2019-07-04 2021-01-05 三菱重工业株式会社 多级离心压缩机

Also Published As

Publication number Publication date
JPH0278788A (ja) 1990-03-19
EP0359514B1 (de) 1992-12-23
DE68904020D1 (de) 1993-02-04
DE68904020T2 (de) 1993-04-29
EP0359514A3 (en) 1990-07-04
CN1041992A (zh) 1990-05-09
US4938661A (en) 1990-07-03
JPH0646035B2 (ja) 1994-06-15
CN1015489B (zh) 1992-02-12

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